Wheel-use bearing apparatus

ABSTRACT

A flange face portion located radially outwardly of boltholes of a flange is formed as a tilting face so that a maximum oppositely-spaced distance α of the flange face portion from a disc rotor is preferably 10 μm. Thereby, minimization is implemented for convex deformation of an outer circumferential end portion of the flange when bolts are press-inserted into boltholes, when nuts are tightened onto bolts, tightening forces compress the disc rotor and the flange to be in close contact and to be fixed-via planar surfaces thereof without clearance being formed therebetween. Consequently, the accuracy of side run-out with surface of the flange can be prevented from being deteriorated.

REFERENCE TO RELATED APPLICATION

This is a divisional application of U.S. patent application Ser. No.10/193,929, filed Jul. 12, 2002, issued on Jul. 26, 2005, as U.S. Pat.No. 6,921,137.

FIELD OF THE INVENTION

The present invention relates to a wheel-use bearing apparatus suitablefor supporting a wheel of vehicles and the like.

BACKGROUND OF THE INVENTION

Hereinbelow, such wheel-use bearing apparatus will be described withreference to FIG. 11. A wheel-use bearing apparatus 1 includes an outerring member 3 mounted on the side of a vehicle body, and a hub wheel 7mounted inward of the outer ring member 3 via double rows of balls 4 and5. The hub wheel 7 is rotatably supported by the balls 4 and 5 on arotational rotational center axis 8. An annular flange 9 projecting in aradially outer direction C of the hub wheel 7 is formed on an outerperipheral surface of a vehicle outer side A of the hub wheel 7. Aplurality of boltholes 10 is formed on a flange surface of the flange 9at the same pitch in a circumferential direction of the flange 9. Bolts11 are respectively press-inserted into the boltholes 10.

Hereinbelow, a wheel mounting structure 2 of the apparatus 1 will bedescribed. A brake disc rotor 12 and a wheel member 13 are provided tooverlap with each other through the bolts 11 as opposed to flange faceof a vehicle outer side A of flange 9. Nuts 14 are threadably tightenedonto the bolts 11. Thus, the structure 2 is configured. The disc rotor12 and the wheel member 13 are fixed with the nuts 14 to the flange 9.

In the wheel mounting structure 2, since the nuts 14 are tightened in alater step, the hub bolts 11 are press-inserted into the boltholes 10 ofthe flange 9. When the bolts 11 are press-fitted to the flange 9,pressing forces cause deformation of peripheral area of press-fittedportions of the bolts 11 of the flange 9. Particularly, an outercircumferential end portion of the flange 9 is deformed convex towardthe vehicle outer side A. Depending on the amount of the deformation,adverse effects can be caused on the accuracy of side run-out withsurface of the flange 9.

SUMMARY OF THE INVENTION

Accordingly, a primary object of the present invention is to provide awheel-use bearing apparatus in which bolts can be fixed into boltholesof a flange not to cause adverse effects on the accuracy of side run-outwith the surface of the flange.

Further objects, features, and advantages of the present invention willbecome apparent from descriptions given hereunder.

In summary, the present invention includes an outer ring member, aninner ring member disposed concentric with the outer ring member, and aplurality of rolling elements provided between the outer ring member andthe inner ring member. A radially-outwardly directional flange is formedon one of the outer ring member and the inner ring member. The flangeincludes a flange face in which boltholes are through-formed and ontowhich a wheel-mounting member is mounted by press-inserting boltsthrough the boltholes. A flange face portion located radially outwardlyof the boltholes in the flange face is formed as a tilting face thattilts such as to be gradually spaced away from the wheel-mounting memberas being closer to an outer circumferential end face of the flange. Thetilting face may be either a curved face or a planar face.

Since the flange face portion is formed as the aforementioned tiltingface, deformation occurring in the flange when the bolts arepress-inserted into the boltholes can be minimized. When nuts aretightened onto bolts, the flange and wheel-mounting member are fixed viaplanar surfaces thereof without clearance. Consequently, the accuracy ofside run-out with surface of the flange can be prevented from beingdeteriorated.

The maximum oppositely-spaced distance is preferably set to 20 μm orshorter. When the distance is set to the value, deformation occurringwhen the bolts are press-inserted into the boltholes can be minimizedeven more effectively.

BRIEF DESCRIPTION OF THE DRAWINGS

These and other objects as well as advantages of the invention willbecome clear by the following description of the preferred embodimentsof the invention with reference to the accompanying drawings, wherein:

FIGS. 1A and 1B are cross-sectional views showing overall configurationsof wheel-use bearing apparatuses according to alternative embodiments ofthe present invention;

FIG. 2 is an enlarged cross-sectional view of an essential portion ofthe configuration shown in FIG. 1;

FIG. 3 is an enlarged perspective view of an essential portion of theconfiguration shown in FIG. 1;

FIG. 4 is an enlarged perspective view of an essential portion of awheel-use bearing apparatus according to another preferred embodiment ofthe present invention;

FIG. 5 is an enlarged perspective view of an essential portion of awheel-use bearing apparatus according to still another preferredembodiment of the present invention;

FIG. 6 is an enlarged perspective view of an essential portion of awheel-use bearing apparatus according to still another preferredembodiment of the present invention;

FIGS. 7A and 7B are cross-sectional views showing the overallconfigurations of wheel-use bearing apparatuses according to stillfurther alternative embodiments of the present invention;

FIGS. 8A and 8B are cross-sectional views showing the overallconfigurations of wheel-use bearing apparatuses according to stillfurther alternative embodiments of the present invention;

FIGS. 9A and 9B are cross-sectional views showing the overallconfigurations of wheel-use bearing apparatuses according to stillfurther alternative embodiments of the present invention;

FIGS. 10A and 10B are cross-sectional views showing the overallconfigurations of wheel-use bearing apparatuses according to stillfurther alternative embodiments of the present invention;

FIG. 11 is a cross-sectional view showing the overall configuration of aconventional wheel-use bearing apparatus.

In all these figures, like components are indicated with the samenumerals.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Hereinbelow, referring to FIGS. 1A to 3, a description will be providedregarding the configuration of a wheel-use bearing apparatus to which apreferred embodiment of the invention is applied. The wheel-use bearingapparatus 1 is used with a driving wheel. The apparatus 1 includes anouter ring member 3 non-rotatably mounted on the side of the vehiclebody. The outer ring member 3 is mounted to a flange 3 a formed toextend in a radially outer direction C on an outer peripheral surfacevia a knuckle (not shown). A hub wheel 7 is supported rotatable on arotational center axis 8 via balls 4 and 5 provided as rolling elementsin double raceways along the axis direction (in the outer ring member3). The hub wheel 7 is an inner ring member for the outer ring member 3.An annular groove 20 is formed in a vehicle inner side B of the hubwheel 7. An inner ring member 21, which is a different member from thehub wheel 7, is engageably fitted to the annular groove 20. The balls 4in the one row use an outer peripheral surface of a body portion 7 a ofthe hub wheel 7 as an inner ring raceway surface, and the balls 5 in theother row use an outer peripheral surface of the inner ring member 21 asan inner ring raceway surface. The wheel-use bearing apparatus 1 as awhole has a configuration of an angular ball bearing with doubleraceways.

Seal members 22 are respectively provided in a vehicle outer side A ofthe balls 4 and in the vehicle inner side B of the balls 5. The sealmembers 22 seal lubricant between the two rows of the balls 4 and 5 andprevent the intrusion of muddy water and the like from the outside.

Hereinbelow, the wheel mounting structure 2 will be described. Anannular flange 9 radially extending in a radially outer direction C isformed on an outer peripheral surface on a vehicle outer side A of thehub wheel 7. In a flange face of the flange 9, boltholes 10 are axiallythrough-formed in, for example, five portions, at the same pitch in thecircumferential direction of the flange 9. Through the boltholes 10,mounting bolts 11, for example, a disc rotor are inserted. An axiallyextending portion 7 b is formed in the vehicle outer side A of theflange 9.

As a circumferentially annular face including the boltholes 10, a flangesurface 10 a on the vehicle outer side A of the flange 9 is formedradially planar. A flange face portion 23 of the flange surface 10 a isformed radially outwardly of the boltholes 10 so as to gradually tilttoward the vehicle inner side B as being closer to the outercircumferential end face of the flange 9. Specifically, the flange faceportion 23 is formed as a tilting planar face that tilts along thecircumferential direction so as be spaced away from the disc rotor 12,which is provided as a wheel-mounting member. The tilting planar face isformed such that a maximum oppositely-spaced distance α from the discrotor 12 on the outer circumferential end face of the flange 9 is 10 μm.

The disc rotor 12 receives a brake force exerted by brake calipers (notshown). A tire wheel member 13 (another wheel-mounting member) isoverlapped with a portion of the disc rotor 12 on the vehicle outer sideA, insertion holes 25 through which the hub bolts 11 are inserted areformed in the disc rotor 12 and the tire wheel member 13, and the discrotor 12 and then the tire wheel member 13 are placed to overlap withthe flange 9. In this state, the nuts 14 are tightened onto theindividual bolts 11, and the disc rotor 12 and the tire wheel member 13are fixed to the flange 9.

When the disc rotor 12 and the tire wheel member 13 are mounted to thewheel-use bearing apparatus 1 in the above-described configuration, thedisc rotor 12 is brought such as to fit to the axially extending portion7 b of the flange 9 on the vehicle outer side A. Concurrently, the discrotor 12 is brought such that the insertion holes 25 thereof are fitonto the bolts 11 preliminarily press-inserted into the boltholes 10 ofthe flange 9. Thereby, the disc rotor 12 is placed to overlap with theflange 9. Similarly, the tire wheel member 13 is placed to overlap withthe disc rotor 12 such that the bolts 11 are inserted into the insertionholes 25. In this state, the nuts 14 are respectively tightened onto thebolts 11, and the disc rotor 12 and the tire wheel member 13 are fixedto the hub wheel 7 (flange 9). The bolts 11 are preliminarilypress-inserted into the boltholes 10 of the flange 9 along the directionfrom the vehicle inner side B to the vehicle outer side A. At this time,in the flange face portion on the vehicle outer side A, the outercircumferential end portion of the flange 9, that is, the portionlocated radially outwardly of the boltholes 10, tends to be deformedconvex toward the vehicle outer side A.

In the embodiment of the invention, the flange face portion 23 locatedradially outwardly of the boltholes 10 of the flange 9 is formed as atilting planar face having a maximum oppositely-spaced distance .alpha.of 10 μm from the disc rotor 12 in the outer circumferential end face ofthe flange 9.

Because of the above-described formation, even in a case where convexdeformation has occurred in the outer circumferential end portion of theflange 9 when the bolts 11 have been press-inserted into the boltholes10 of the flange 9, the deformation can be reduced by a certain degree.Consequently, the amount of convex deformation occurring when the bolts11 are press-inserted into the boltholes 10 is reduced small withrespect to the flange face on the vehicle outer side A. For example,suppose a convex deformation of 30 μm can occur when the press-insertionof the bolts 11. In this case, when a tilting face as described above isformed, a convex deformation of at most 20 μm remains.

Thereby, the state where the portion of the boltholes 10 in the flange 9is made concave in comparison to the convex portion can be maintained,and the amount of the convex deformation can be reduced to be of anoptimal value.

When the nuts 14 are respectively tightened onto the bolts 11 in theabove-described state, a tightening force thereby exerted works to fixthe disc rotor 12 and the flange 9 via the planar faces thereof that arecompressed to be in close contact with each other without clearancetherebetween. Thereby, the accuracy of side run-out with the surface ofthe flange 9 can be prevented from being deteriorated.

Table 1 shows results of experiments regarding the amounts of siderun-out with the surface in a case where the hub wheel 7 is rotated onrotational center axis 8.

TABLE 1 Conventional Example Shape Direct Embodiment Measuring Meas-Plate-Using Direct Plate-Using Method urement Measurement MeasurementMeasurement N 100 100 100 100 Max 21.8 23.0 18.4 14.2 Min 3.2 1.6 3.81.2 Average 9.74 8.15 9.41 6.45 Standard 3.60 4.45 2.94 2.98 DeviationCmk 0.37 0.39 0.47 0.72 In Table 1, the column items represents asfollows: N = Number of experiments Max = Maximum value of run-out amount(μm) Min = Minimum value of run-out amount (μm) Average = Average valueof run-out amounts (μm) Standard Deviation = Standard deviation inrun-out amount Cmk = Process capability

The direct measurement refers to measurement in a case where the outerring member 3 is fixed, and the hub wheel 7 is rotated on the rotationalcenter axis 8 in a state where the bolts 11 are press-inserted into theboltholes 10 of the hub wheel 7. The plate-using measurement refers tomeasurement in a case of using plates (not shown) as substitutes for thedisc rotor 12 and the tire wheel member 13.

Table 1 verifies that the Cmk can be improved and the run-out amount ofthe disc rotor 12 is reduced according to the configuration in which, inthe flange face portion of the flange 9, the flange face portion 23located radially outwardly of the boltholes 10 is formed as the tiltingplanar face that gradually tilts toward the vehicle inner side B asbeing closer to the outer circumferential end face of the flange 9; andconcurrently, the flange face portion 23 is formed such that the maximumoppositely-spaced distance α from the disc rotor 12 on the outercircumferential end face of the flange 9 is 10 μm.

Hereinbelow, another embodiment of the invention will be described withreference to FIG. 4. According to the above-described embodiment, in theflange face portion of the flange 9, the flange face portion 23 locatedradially outwardly of the boltholes 10 is formed as the tilting planarface that gradually tilts toward the vehicle inner side B as beingcloser to the outer circumferential end face of the flange 9; andconcurrently, the flange face portion 23 is formed such that the maximumoppositely-spaced distance α from the disc rotor 12 on the outercircumferential end face of the flange 9 is 10 μm. However, in thepresent embodiment, in addition to the above-described arrangement, aflange face portion 24 located radially inwardly of the boltholes 10 isformed as a tilting planar face that gradually tilts toward the vehicleinner side B as being closer to the center of the hub wheel 7; andconcurrently, the flange face portion 24 is formed such that a maximumoppositely-spaced distance β from the disc rotor 12 in an end positionthereof (base end portion of the flange 9) is 10 μm (as shown by virtuallines in FIGS. 1B, 7B, 8B, 9B and 10B). In this embodiment, an annularface 10 a is formed planar to include boltholes 10 provided along thecircumferential direction and to have the same width as the diameter ofeach of the boltholes 10. Other configurations are the same as those ofthe embodiment described first.

The present embodiment is effective in the configuration in which theradially outer side and the radially inner side of the boltholes 10 aredeformed convex when the bolts 11 are press-inserted into the boltholes10 of the flange 9. Similar to the configuration of the firstembodiment, in comparison to the shape of the conventional flange 9, ithas been verified that the Cmk can be improved, and the accuracy of siderun-out with the surface of the disc rotor 12 can be prevented frombeing deteriorated.

The invention is not limited to the configuration in which the flangeface portion 23 or the flange face portion 24 is formed to have theannular face along the circumferential direction of the flange 9. Asshown in FIG. 5, only the radial outer face in an outer circumferentialportion of each of the boltholes 10 may be formed in the form of atilting planar face 26 that tilts toward the vehicle inner side B.Alternatively, depending on the case, as shown in FIG. 6, the overallouter circumferential portion of each of the boltholes 10 may be formedas a tilting planar face 27 that tilts toward the vehicle inner side Band that is circularly concentric with the bolthole 10. In any of thecases, operational advantages similar to those of the above-describedembodiments can be achieved. The tilt amount of each of the tiltingplanar face 26 and the tilting planar face 27 is set similar to that ofeach of the above-described embodiments. Although the tilting planarface is formed on the flange 9 in each of the above-describedembodiments, the present invention is not limited thereby. Instead ofthe tilting planar face, a tilting curved face may be formed to bespaced away from the disc rotor 12 as in the case of the tilting planarface. Also in this case, the accuracy of side run-out with the surfaceof the disc rotor 12 can be prevented from being deteriorated, as in thecase of each of the above-described embodiments.

In the above-described embodiments, the tilting planar face or thetilting curved face is formed such that the maximum oppositely-spaceddistanced from the disc rotor 12 is 10 μm. However, even with a maximumoppositely-spaced distanced set in a range of from 20 to 10 μm, theaccuracy of side run-out with the surface of the disc rotor 12 can beprevented from being deteriorated, as in the case of each of theabove-described embodiments.

In the above-described embodiments, description has been made withreference to the configuration in which the hub wheel 7 (inner ringmember) is supported by the outer ring member 3, which is fixed to thevehicle body, to be rotatable on the rotational center axis 8 via thedouble rows of the balls 4 and 5 provided as rolling elements. However,the invention is not limited to this configuration and may of course beapplied to a wheel-use bearing apparatus 1 (used with a driving wheel)shown in FIGS. 7A and 7B. Specifically, axial two rows of inner ringmembers 30 are non-rotatably supported in the side of the vehicle-bodyside, and an outer ring member 31 is formed rotatable on the rotationalcenter axis 8 via double rows of balls 4 and 5. A flange 32 radiallyoutwardly extending is formed on the outer ring member 31, bolts 33 arepress-inserted into the flange 32. Also in this case, the maximumoppositely-spaced distance α from a disc rotor 12 in the outercircumferential end face of the flange 32 or the maximumoppositely-spaced distance β in the base end portion of the flange 32 isset similar to that in the respective embodiment described above.Thereby, even when the bolts 33 are press-inserted into the flange 32,the accuracy of side run-out with the surface of the disc rotor 12 canbe prevented from being deteriorated.

The present invention may also be applied to other types of wheel-usebearing apparatuses 1 as those to respectively be provided as hub unitsshown in FIGS. 8 to 10, each including a hub wheel 7 formed rotatable ona rotational center axis 8 via rolling elements in an outer ring member3 mounted on the vehicle-body side.

Among these wheel-use hearing apparatuses 1, ones shown in FIGS. 8A and8B are used with a driven wheel and are configured as follows. Innerring members 21, 21 with double raceways are supported in an outer ringmember 3 mounted in the vehicle-body side to be rotatable on arotational center axis 8 via rollers 35, 35 provided as rollingelements. A hub wheel 7 is inserted into the inner ring members 21, 21and an axial end portion of the hub wheel 7 is caulked onto an end faceof the end face of one of the inner ring members 21. A waterproof cover36 is mounted onto an end portion of the outer ring member 3, a flange 9is formed on the hub wheel 7, and bolts 11 are press-inserted into theflange 9.

The wheel-use bearings 1 shown in FIGS. 9A and 9B are used with a drivenwheel and are configured as follows. An inner ring member 21 is fittedinto an outer ring member 3 mounted in the vehicle-body side. A hubwheel 7 and the inner ring member 21 are supported in the outer ringmember 3 to be rotatable on a rotational center axis 8 via balls 4 and 5with double raceways and a nut N is tightened on an end portion of thehub wheel 7. A cover 37 is mounted onto the outer ring member 3 toprevent muddy water or the like from flowing to a vehicle speed sensor(not shown). A flange 9 is formed to the hub wheel 7, and bolts 11 arepress-inserted into the flange 9.

The wheel-use bearings 1 shown in FIGS. 10A and 10B are used with adriven wheel and are configured as follows. An axial portion 41 isformed integrally with a cup-shaped outer ring member 40 provided as aconstant-velocity universal joint, and is inserted into a hub wheel 7,and an end portion of the axial portion 41 is caulked. The hub wheel 7and the cup-shaped outer ring member 40 are supported in an outer ringmember 3 to be rotatable on a rotational center axis 8 via double rowsof balls 4 and 5. A flange 9 is formed to the hub wheel 7, and bolts 11are press-inserted into the flange 9.

Also in the wheel-use bearing apparatuses 1 shown in FIGS. 8A, 8B, 9A,9B, 10A and 10B, the maximum oppositely-spaced distance α from a discrotor 12 in the outer circumferential end face of the flange 9 or themaximum oppositely-spaced distance β in the base end portion of theflange 9 is set similar to that in the respective embodiment describedabove. Thereby, even when the bolts 11 are press-inserted into theflange 9, the accuracy of side run-out with the surface of the discrotor 12 can be prevented from being deteriorated.

While there has been described what is at present considered to bepreferred embodiments of this invention, it will be understood thatvarious modifications may be made therein, and it is intended to coverin the appended claims all such modifications as fall within the truespirit and scope of this invention.

1. A bearing apparatus for mounting a wheel to a vehicle and to supporta brake disc, said bearing apparatus having an inboard side facing saidvehicle when said bearing apparatus is mounted to said vehicle and anoutboard side opposite from said inboard side, comprising: an outer ringmember non-rotatably mountable to said vehicle by a mounting structureconnected to the outer ring member; an inner ring member that isdisposed concentric with said outer ring member about a center axis; aplurality of rolling elements provided between said outer ring memberand said inner ring member; a hub wheel having a radially-outwardlyextending flange, the hub wheel being inserted in said inner ring memberand having an axial end face caulked to said inner ring member; saidflange of said hub wheel having a flange face in which boltholes arethrough-formed and onto which the brake disc is mounted by bolts pressinserted through the boltholes, said flange face being on said outboardside of said bearing apparatus; and said flange face having a recededflange face portion extending radially outward from radially outermostcircumferential points of said boltholes with respect to said centeraxis, said receded flange face portion being increasingly receded from aplane perpendicular to said center axis with increasing radial distancefrom said center axis.
 2. A bearing apparatus for mounting a wheel to avehicle and to support a brake disc, said bearing apparatus having aninboard side facing said vehicle when said bearing apparatus is mountedto said vehicle and an outboard side opposite from said inboard side,comprising: an outer ring member; an inner ring member that is disposedconcentric with said outer ring member about a center axis; a pluralityof rolling elements provided between said outer ring member and saidinner ring member; a flange fixedly connected to one of said outer ringmember and said inner ring member to rotate with said one of said outerring member and said inner ring member, and said flange having a flangeface in which boltholes are through-formed and bolts press insertedthrough the boltholes, said flange face being on said outboard side ofsaid bearing apparatus; a mounting member for mounting the bearingapparatus to the vehicle, the mounting member being fixedly connected toanother one of said outer ring member and said inner ring member; andsaid flange face having a receded flange face portion extending radiallyoutward of said boltholes with respect to said center axis, said recededflange face portion being increasingly receded from a planeperpendicular to said center axis with increasing radial distance fromsaid center axis, wherein said receded flange face portion extendsradially outward from radially outermost circumferential points of saidboltholes.
 3. The bearing apparatus according to claim 2, wherein thebrake disc is fixed to the flange face such that said brake disc lies onat least a portion of said flange face and is fixed by the bolts pressinserted through the boltholes, and nuts are tightened onto the bolts tofix the brake disc.
 4. The bearing apparatus according to claim 2,wherein said receded flange face portion is an annular face formed acircumferentially around said flange.
 5. The bearing apparatus accordingto claim 4, wherein said annular face is frustoconical.
 6. The bearingapparatus according to claim 2, wherein said receded flange face portionincludes annular portions around said boltholes.
 7. The bearingapparatus according to claim 6, wherein said annular portions arefrustoconical and formed circularly concentric with said boltholes. 8.The bearing apparatus according to claim 2, further comprising an innerreceded flange face portion extending radially inward from radiallyinnermost circumferential points of said boltholes, said inner recededflange face portion being increasingly receded from a planeperpendicular to said center axis with decreasing radial distance tosaid center axis.
 9. The bearing apparatus according to claim 8, whereina maximum distance of recession of said inner receded flange faceportion is set to 20 μm or less.
 10. The bearing apparatus according toclaim 1, wherein the brake disc is fixed to the flange face such thatsaid brake disc lies on at least a portion of said flange face and isfixed by the bolts press inserted through the boltholes, and nuts aretightened onto the bolts to fix the brake disc.
 11. The bearingapparatus according to claim 1, wherein a maximum distance of recessionof the receded flange face portion is set to 20 μm or less.
 12. Thebearing apparatus according to claim 1, wherein said receded flange faceportion is an annular face formed a circumferentially around saidflange.
 13. The bearing apparatus according to claim 12, wherein saidannular face is frustoconical.
 14. The bearing apparatus according toclaim 1, wherein said receded flange face portion includes annularportions around said boltholes.
 15. The bearing apparatus according toclaim 14, wherein said annular portions are frustoconical and formedcircularly concentric with said boltholes.
 16. The bearing apparatusaccording to claim 1, wherein said receded flange face portion extendsradially outward from radially outermost circumferential points of saidboltholes.
 17. The bearing apparatus according to claim 1, furthercomprising an inner receded flange face portion extending radiallyinward from radially innermost circumferential points of said boltholes,said inner receded flange face portion being increasingly receded from aplane perpendicular to said center axis with decreasing radial distanceto said center axis.
 18. The bearing apparatus according to claim 17,wherein a maximum distance of recession of said inner receded flangeface portion is set to 20 μm or less.
 19. The bearing apparatusaccording to claim 2, wherein a maximum distance of recession of saidinner receded flange face portion is set to 20 μm or less.